Axially aligned rotationally adjustable flow contol valve

ABSTRACT

A rotationally adjustable valve is disclosed whereby the user is able to control the flow of fluids from complete shutoff to maximum flow by rotating the adjustment means of the valve, said rotation being axial to the flow of the fluid. Additionally, the user is able to attach high and low pressure test probes directly to the valve, as it is rotatably adjusted, so that additional equipment is not required next to the valve. An embodiment of this invention includes the use of an adjustable Cv disk to set the maximum flow of the valve, rather than just create a simple 180° on/off, very similar to a current 90° ball valve that this device will replace.

This application is a continuation of U.S. application Ser. No.14/457,120, now U.S. Pat. No. 9,476,509, which is a continuation-in-partof co-pending U.S. application Ser. No. 14/243,611 filed on Apr. 2,2014, now U.S. Pat. No. 9,400,057.

FIELD OF THE INVENTION

The field of this invention is the heating ventilation and cooling(HVAC) industry where fluids are the medium for the heating and cooling.Fluids that are sent from boilers or chillers are routed through pipingstructures which need to be balanced in terms of pressure and flow inorder to even distribute the hot or cold fluids into air handler unitswhich deliver temperature controlled air. In this industry, quarter-turnball valves are usually used which present a host of problems andrestrictions on their location and use.

BACKGROUND OF THE INVENTION

This device is used in piping system in large HVAC systems where thecontrol of the amount of flow is desired. Currently, most controls thatregulate the flow in piping systems are based on the principle shown inthe quarter-turn ball valve, where the operator can have completeshutoff or full flow within a 90° turn of the handle. In the field ofpower assisted actuators, most all of the manufactures design them forthe same quarter-turn application as well. Generally in this industry, afull port or more commonly known full bore ball valve is incorporatedinto the piping structures. This valve has an over-sized ball so thatthe hole in the ball is the same size as the pipeline resulting in lowerfriction loss.

There are many problems with the basic ball valve involve its inabilityto regulate evenly as the valve is opened or closed. This means thatsimply opening the ball valve a certain percentage of the total range,say 50% for example, does not equate to 50% of the total flow of thevalve. This non-linear relationship between the percentage open andpercentage of flow creates problems in setting the flow into aparticular section of the piping system. This is because of the shape ofthe insert being circular. This non-linear problem can be greatlyimproved with the additional of a parabolic or other characterizedinsert into the ball opening itself.

In the disclosed invention, a venturi tubes is used to calculatepressure differential and thus fluid flow. With a ball valve, to thenature of the throttling or jetting aspects of the ball as it rotates atlow percentages of openness, it is very difficult to accurately measureflow anywhere near the valve. This leads to oversizing of the pump andrunning the pump at a higher pump rate to compensate for theinefficiencies of a ball valve. A venturi is used whenever low pressureloss and high accuracy is desired, and due to the nature of the valvedisclosed herein, the length of straight piping is greatly reduced asthe pressure differential measuring means are located directly upon thevalve as this valve incorporates a venturi. Due to the low pressureloss, a venturi saves the user many dollars and frequently pays foritself in one year of continuous operation by greatly reducing pumpingcost.

Other problems associated with ball valves is the amount of forcenecessary to open or especially close the valve when under pressure asthe flow of fluid fights against the closing or opening of the valve.Especially when one is trying to barely crack open the valve to let inonly a minimal amount of flow. Also, due to the characteristics of theflow opening and exit of the ball itself, at low flow rates, that is atremendous amount of cavitation and noise exist if the pressuredifferential is substantial across the ball itself. The critical flow ina ball valve is encountered when delta P (the differential pressure) is0.15 P, which is far below the usual figure of 50% of absolute inletpressure. Another issue is the handle to adjust the opening of the ballitself, as it must be located in a position where the user can accessit. In piping structures where many pipes are located and space is at apremium, the knuckles of more than one person has been wracked againstthe piping structure when attempting to access and adjust a ball valve.Where pressures are significant, the size and length of the handlebecomes a critical aspect of the operation of the valve and the need forspace can drastically increase.

The current state of the art can be found to use ceramic disks that haveangular segments removed that allow for the flow of fluids. Theseceramic disks are used to regulate the flow of fluids in manyapplications, such as high end water faucets and shower fixtures. U.S.Pat. No. 7,841,362 issued to Kim on Nov. 30, 2012 shows the use ofmultiple disks in a faucet or water control valve, where temperature andflow are controlled. This disclosure is typical of the faucet style ofcontrol valves, where two sources of fluid are mixed and flow iscontrolled. These valves have the discharge of fluid through a spoutwhich is basically perpendicular to the flow of the fluid. Prior artdoes exist to detail that ceramic disks can be used to supply anddischarge fluids as well as U.S. Pat. No. 7,373,950 issued to Huang onMay 20, 2008 demonstrates where a single set of disks control the mixingof hot and cold water from two distinct sources and regulates theoutbound flow of water through the same disks.

One of the deficiencies of the current state of the industry as well asthe prior art is that a valve, that can go to complete shutoff andmaximum flow with a 90 degree rotation about the axis of fluid flow,cannot also be capable of measuring the differential pressure betweenthe inlet and outlet of the valve. Current ball valve technology, whichthrough the use of parabolic or other inserts to the ball can approach amore linear relation between the percentage of openness of the ball tothe percentage of maximum flow through the valve, does not have thecapabilities to have a pre-set Cv in association with the ball valve.

Additionally, due to the surfaces upon which the fluids impact upon whenthe ball valve is turned and due to the close tolerances required toprevent fluids from leaking past the ball portion of the valve, it isimperative that the fluids be free from any hard impurities that canscratch or mar the surface of the ball and that can damage the exposedO-Rings. Furthermore, since the O-Rings are exposed to the fluids on adaily basis, the chance for O-Ring degradation due to reactions with thefluids is greatly enhanced, leading to failure and leakage. To preventthis possible degradation, some manufactures use Teflon seals whichfacilitate a sealing function as well as creating a surface with lessfriction than O-rings.

Another issue with using ball valves is that the user most stillincorporate a venturi and high and low pressure test probes to measurethe flow of the fluid. Since cavitation and throttling may occur withthe use of a ball valve, the venturi must be location a sufficientdistance away from the ball valve in order to more accurately measurethe flow. This could cause problems in the reading and adjusting theflow in a particular section of a piping structure.

It is an object of this invention to create a device that will enablethe user to adjust the flow of fluid in a piping structure where spaceis at a premium and where accuracy of the fluid flow is critical.

It is a further object of this invention to provide the user with avalve whose adjustment is axially relation to the flow of fluid. Thisaxial relationship provides for a more compact unit and which moreaccurately controls the flow using linearly related flow control disks.

It is a further object of this invention to provide a device with whichthe user can measure the differential pressure as the device is beingoperated so that flow can be accurately measured at the actual valve asit is being adjusted. It is desirable that the space required for thismeasurement be compact in nature and close to the body of the valve forthe most accurate measurement as well as being compact for the tightspaces that it will likely be experiencing.

It is a further object of this invention to provide an embodiment ofthis device where be a Cv can be set for this valve, through the use offlow control disks, whereby the user has an axially controlled valvewith a set maximum Cv, said valve being able to go to complete shutoff.

Accordingly, it is the goal of this invention to create an adjustablevalve that is axially related to the fluid flow, containing port todetermine the actual flow of the fluid, that has the aforementionedcharacteristics of simplicity, accuracy, adaptability to current usesand safety.

BRIEF SUMMARY OF THE INVENTION

Accordingly, this application discloses a valve that is adjusted axiallyalong the axis of the flow of fluid. This valve is adjusted by therotation of the body of the valve where the valve is part of a pipingstructure. Along with the adjustment portion, there is also the additionof two test ports for high pressure and low pressure measurement, saidports being integral with the rotational member. The valve rotatesthrough 180° from a complete shutoff to maximum flow and back tocomplete shutoff within the 180°. The valve is able to be rotated simplyby hand control and does not need any tool due to the design of theinterface between the control disks and the minimal need for O-ringsinterference. Furthermore, the valve has a set screw that is attached toan external boss, which is used to lock the valve in place and preventany unwanted rotation. The valve either has a stop at 180°, so that theuser cannot continue past 180° or the valve does not have a stop andallows the user to then complete the rotation for the full 360°. Asstated, test ports are integral with the rotating member so that thereis an instant feedback of the pressure differential between the highside and the low side of the valve so that one can calculate flow. Sincethis valve design does not permit increases in cavitation or turbulentflow in the piping system, it is possible to measure the pressuredifferential at a location that is very close to the actual adjustmentmeans, which is one of the drawbacks with normal ball valves.

The valve has two control disks, one stationary and one that is movableand it is the interface between openings on both disks that allow theuser to select a particular flow rate. Due to the smoothness of thedisks, which are preferably made of ceramic materials, the frictionmoment is greatly reduced even under high pressure fluid flow.

As an embodiment the user can incorporate an adjustable Cv control diskinto the valve so that the maximum Cv or maximum flow rate can beestablished for the valve. This allows the user to set the flow rate andalso allows the system to be able to anticipate the maximum flow comingout of the valve.

Another embodiment is the addition of a larger Cv control surface whichwill enable the valve to rotate through up to a total of 300° ofrotational movement. This allows a user to more finitely adjust thevalve over a larger rotational range and can accommodate higher Cvvalues. The 300° degrees of rotation is not a limiting factor thisinvention, but rather a range of motion that will be most suitable forthe application in HVAC piping structures.

BRIEF DESCRIPTION OF SEVERAL VIEWS OF THE DRAWINGS

In FIG. 1, in a view of the valve where the viewer is looking into thetest ports of the device. This will be called the upper view.

In FIG. 2, the view is of the inlet side of the valve with the testports pointing downwardly.

In FIG. 3, the view is of the outlet side of the valve with the testports pointing downwardly.

In FIG. 4, an upper oblique view of the valve is shown with the outletof the valve being exposed.

In FIG. 5, a side profile view of the valve is shown with a cutaway viewthrough the body of the valve is shown detailing the inlet portion ofthe valve and the first metering section.

In FIG. 6, a side profile view of the valve is shown with a cutaway viewthrough the body of the valve is shown detailing the regulating meansand the outlet portion of the valve.

In FIG. 7 through FIG. 10, is a series of views looking at the valvefrom the inlet side, where the valve has been adjusted to various flowamounts, as shown as a percentage of total flow. One can observe thedifferent regulating means as they interact with one other by thedifference in the cross hatching.

In FIG. 11, a detail of only the outlet portion of the valve is shownalong with the primary flow control regulating means.

In FIG. 12, a detail of only the outlet portion of the valve is shownalong with the secondary flow control regulating means, where theprimary flow control regulating means has been removed from the view forclarity.

In FIG. 13, an oblique view of the valve is shown where the outletportion has been removed and only the primary flow control regulatingmeans is shown.

In FIG. 14, an oblique view of the valve is shown where the outletportion has been removed and the primary flow control regulating meansis also removed to detail the inner bore of the body of the valve

In FIG. 15 and FIG. 15A, the primary flow control disk is shown in afrontal and an oblique view respectively, where the disk is used in anapplication where the valve is capable of complete shutoff every 180°degrees.

In FIG. 16 and FIG. 16A, the secondary flow control disk is shown in afrontal and an oblique view respectively, where the disk is used in anapplication where the valve is capable of complete shutoff every 180°degrees.

In FIG. 17 and FIG. 17A, the variable Cv or variable flow regulatingcontrol disk is shown in a frontal and an oblique view respectively,where the disk is used in an application where the valve is capable ofcomplete shutoff every 180° degrees.

In FIGS. 18 and 18A, the primary flow control disk is shown where theembodiment of having a range of motion greater than 180°.

In FIG. 19 and FIG. 19A, the variable Cv or variable flow regulatingcontrol disk is shown in a frontal and an oblique view respectively,where the disk is used in an where the embodiment of having a range ofmotion greater than 180°.

In FIG. 20, the 2 piece embodiment of the axial valve is shown on theleft side elevation of the valve detailing the high pressure port.

In FIG. 21, the 2 piece embodiment of the axial valve is shown on theright side elevation of the valve detailing the low pressure port.

In FIG. 22, the top elevation of the 2 piece embodiment of the axialvalve is shown.

In FIG. 23, a frontal oblique view of the right side of the 2 pieceembodiment of the axial valve is shown, detailing the adjustment slotand screw.

In FIG. 24, the top elevation is shown of the 2 piece embodiment of theaxial valve where cross-sectional dividing lines are shown.

In FIG. 25, the cross-sectional view of the 2 piece embodiment of theaxial valve is shown viewing the interior of the valve from the leftside.

In FIG. 26, the cross-sectional view of the 2 piece embodiment of theaxial valve is shown viewing the interior of the valve from the rightside.

In FIG. 27, a portion of the cross-sectional view of the 2 pieceembodiment of the axial valve is shown viewing the interior of the valvefrom the right side detailing the adjustment carrier.

DETAILED DESCRIPTION OF THE INVENTION

This invention as disclosed in the drawings has the principle use in theHVAC environment but there exists no limiting language to prevent thisinvention to be practiced in other fields of use. The invention consistsof three main elements, inlet section, a body and an outlet portion.This invention is an adjustable valve that is adjusted axially to theflow of the fluid, with the further embodiments of ports that aredesigned to report differential pressure through the valve and wherebythe Cv of the valve can be set and still have the valve go to completeshutoff.

In FIG. 1, the valve is shown with its three main sections; a centralbody 100, an inlet portion 200 and an outlet portion 300. Shown in thisview are differential pressure measurement means, shown as ports 102 forhigh side pressure and port 103 for low side pressure. It is disclosedthat this invention will function without ports 102 and 103 as themeasurement of differential pressure across this valve can be donethrough the use of other independent devices. It can be seen in thisFIG. 1 that high side pressure test port 107 is at the base of high sidepressure monitoring port 102. Similarly, low side pressure test port 106is located at the base of low-pressure test port 103. Both ports 102 and103 are internally adapted, by threads or other means, to acceptindustry standard pressure probes, which can include those probes thatare capable of measuring pressure and temperature. Located between inletportion 200 and high pressure port 102 is set screw boss 104 thereinlocated on boss 104 is threaded set screw through hole 112. It is theprocedure for the user to adjust the device to the desired flow, andthen use the set screw to lock it in place preventing further rotation.Located appurtenant to outlet 300 is angular displacement index 105which corresponds in 90° increments to major angle indicator 106. It isthe relation of the increments on index 105 to angular displacementguide 310 that is located on outlet portion 300, so that the user canreference the amount of rotation that has been accomplished through anumber of degrees. Guide 310 is located upon the hex-nut 301. Bothoutlet hex-nut 301 and inlet hex-nut 201 are shown as hexagonalconnecting members, but there is nothing in this application thatdefines and/or limits the shape or size of either of the flanges. Body100 is defined as a cylindrical member 101 that can either have a smoothor polygonal exterior surface. Inlet portion 200 and outlet portion 300defined the two ends of the cylindrical member 101, where the inletportion 200 is defined as the proximal end and the outlet portion 300 isdefined as the distal portion.

It is in FIG. 2, that the valve is shown with inlet portion hex-nut 201facing the observer. As references one can see set screw boss 104 andhigh pressure test port 102. In this view primary control disk 113 isseen in its closed position. The opening that defines inner bore 203 isdefined as sharing a common central axis to the cylindrical member 101.Inlet lead-in bevel 206 allows the operator to more accurately insertthe connecting member into the body. It is noted that the piping systemconnection means are located at the distal end of inlet section 200 andoutlet portion 300 respectively, are not adapted to any particularpiping structure connecting means. In this embodiment of this invention,connection means are internally threaded couplings which have adescribed hexagonal external interface, which is commonly known in theplumbing industry as inlet hex nut 201 and outlet hex nut 301, which arelocated at the distal end of inlet section 200 and outlet portion 300respectively. This device, though commonly using national pipe threadthreads, can be adapted to a piping system by a sweated or swaged jointsor any other common plumbing practice joinery. In FIG. 3 we see theopposite end from FIG. 2 as hex-nut 301 is shown, and low-pressure port103 is shown for reference. Secondary control disk 315 is shown andprimary control disk 113 is shown as well. It is the relationshipbetween the two that details that is in a closed position as the twocontrol disks are diametrically opposed in their position. Interior bore303 has a common bore that is coincident to bore 203 and outlet lead inbevel 317 assists the operator in inserting the piping joints. FIG. 4 isan oblique view of the upper portion of the valve. Reference is madethroughout this application as the upper portion of the valve as beingthat portion containing the high pressure and low pressure ports 102 and103. FIG. 4 details the outlet bore 303 along with lead in bevel 317along hex-nut 301.

FIG. 5 is a cutaway version of the valve which details the inlet portionas well as the first half of the main body. Lead-in bevel 206 is locatedabout the entrance of bore 203. Further interiorly located in the centerof opening of bore 203 is stepped down region 207 which providesentrance to the venturi 204. The venturi is a commonly used device inthe plumbing industry. The venturi allows for the measurement of thevolumetric flow rate of the fluid going through the valve as there is adirect relationship between the high side and the low side pressuredifference and the fluid speed through the valve, where fluid flowincreases as the cross-sectional area decreases, which is based onBernoulli's principles. This step down from bore 203 to the entrance ofventuri 204 is shown as rough steps which is common for manufacturing tocreate a bore pattern using smooth sides and sharp corners as that isthe shape of the boring tool. There is nothing that prevents thedisclosure of a smoother transition between board 203 and venturi 204.Venturi wall 209 is a conically described section which terminates atthe proximal end of inlet portion 200 along inlet portion terminationwall 208. Inlet portion 200 fits into main body 100 along the commonbore between the two parts. Along the interior of inlet portion 200 issnap ring groove 211 which holds snap ring 202, said snap ring 202secures the inlet portion 200 onto body 100. Inlet portion 200 buttsagainst body 100 along the joint between the interior flange wall 210and body exterior collar 121. Distal portion 109 of body 101 containsO-ring groove 124. The O-ring that sits in O-Ring groove 124 is notshown so as to maintain the clarity of the drawing. Venturi 204terminates into low-pressure sensing ring as part of body 101. It isseen in FIG. 5 high-pressure testing port 107 is in direct contact andrelations there with circular venturi sensing ring 108 so that the lowpressure can be measured. High-pressure port 102 is shown with smoothwalls but is designed to adapt to any size and or connection type,including the common NPT thread, that is available on the testingprobes. Though desirable to remain located with the valve, the testingprobes can be removed and used on other applications. After the fluidpasses through sensing ring 108 it is throttled down through throttlingarea 110 after which the now higher pressure fluid flows into interiorchannel 111 prior to the fluid de-throttling into primary control disk113. The fluid flow through interior channel 111 is at a higher pressurethan it was going through the low-pressure sensing ring. It is at theend of channel 111 that low-pressure sensing port 106 is seen on FIG. 6.

FIG. 6 details the outlet and of the valve. Primary control disk 113 isplaced upon O-ring that is compressed upon in O-ring groove 126 by disk113 as disk 113 is tightly fit and secured into primary disk enclosure130, where the purpose of the O-ring is to seal the disk preventingblow-by of the fluids as well as to promote contact with the secondaryflow control disk 315 through the compressive and expansivecharacteristics of a circular sectioned O-Ring. Again the O-ring isexcluded for purposes of clarity. Primary control disk 113 has twolocating tabs 117 located 180° opposite along the exterior of theprimary control disk 113. Tabs 117 of primary disk 113 are securelylocated into primary disk securement slots 125 located on body 101 asmore clearly seen in FIGS. 13 and 14. FIG. 6 also shows rotation stop312 which is placed to prevent rotation of the body 100 past a setnumber of degrees, which in this case would be 180°. The valve uses therotation stop as a convenience versus a necessity as there is no harm tothe valve should the user completely rotate the body 360° except forissues with the differential pressure probes.

Outlet portion 300 has centered through it bore 303 which has a commonaxis with bore 203 and channel 111, lead-in bevel 317 being centeredabout bore 303, which has a similar step down region 305 that has sharpside, again referring to common tooling nomenclature of the industry.Region 305 steps down into central outlet bore 304 which is in fluidcommunication with secondary control disk 315. Secondary control disk315 also has locking flanges 308 which slide into slot 316 which holdsdisk 315 in place. As with the primary control disk 113, secondarycontrol disk 315 also is tightly fit and secured into secondary diskenclosure 321 and compresses upon an O-ring that fits into O-ring groove306, the O-ring is not shown for purposes of clarity and adapts thecharacteristics of sealing and compressive resistance as the O-Ringprovides to the primary control disk 113. It can be shown that snap ring316 sits in groove 302 of the outlet portion 300 and interfaces withbody 101 through snap ring channel 119. This snap ring secures outletportion 300 into body 100. Located interiorly from snap ring 316 isO-ring groove 116 which provides additional sealing for outlet portion300, as before O-ring is not shown for purposes of clarity. All O-ringsused in this device are common O-rings with a circular cross-sectionthat are used in the industry, constructed of a material that does notdegrade in the presence of the proposed fluids going through the about.In this case buna-nitrile, silicon or EPDM O-rings can be used, as wateris the proposed fluid. Proximal edge 318 of outlet portion 300 butts upagainst outside flange wall 121 and there is a close fit tolerancebetween interior bore wall 307 of outlet portion 300 and the interiorwall 123 of body 101. Though it is shown on FIG. 6 that primary controldisk 113 and secondary control disk 315 are not in contact, this is forpurposes of clarity of the drawing. In actual application O-rings thatare contained in O-ring grooves 126 and 306 will maintain the controldisks in constant contact. Furthermore the pressure and flow of thewater will push the disks together further preventing any leakagebetween the deaths The two control disks are ground smooth and have asurface roughness of no greater than 0.2 of a micrometer.

FIGS. 7, 8, 9 and 10 show the relationship between the primary and thesecondary control disks 113 and 315 respectively. Being viewed from theinlet hex-nut 201 as the valve body rotates one can see how the primarycontrol disk shown with the wavy lines rotates through the stationarysecondary control disk shown with the straight lines.

FIG. 11 is a view of the outlet portion 300 as can be seen the interiorbore wall 307 defines the piece. Snap ring groove 302 a shower and atthe proximal and the distal and is defined by termination wall 313.Primary control disk 113, though not being part of the outlet portions300, is shown for reference only. One can see the tab 117 as well as thedefined opening 120. Shown in this view is rotation stop 312 which canbe used if the purchaser of the product wants only 180° rotation or anyspecified angle as we will see later that the maximum rotation is 300°.The maximum of 300° rotation is not a limiting feature of thisinvention. The shape of the openings in the secondary disk 315 can beadapted to any finite number of degrees, but it found that in thepracticing of this invention in the HVAC industry, approximately 300degrees of rotation would be the most adaptable to the application ofthis invention. Rotation more than 330 degrees might cause issues withtest probes inserted into the test ports 102 and 103 along with problemsassociated with the secondary disk 315. It is important that the user beable to have a positive stop to know when the valve is flowing at itsmaximum or minimum valves. FIG. 12 is the same view as FIG. 11 scansprimary control disk 113. Secondary control disk 315 is shown flush withtermination wall 313 as disk 315 is positioned into disk enclosure 321,where disk enclosure 321 contains O-ring groove 306. Secondary controldisk 315 being held in place by tabs 308 which fit in the slot 316. Ascan be observed between FIG. 11 and FIG. 12 the opening 120 of primarycontrol desk 113 interfaces with the closed portion of secondary controldisk 315. This would be in the closed state.

FIG. 13 is a view of the body and inlet portion distally related to thebore of the body. As can be seen the outlet portion 300 has been removedso that we can observe the inside of body 101. Primary control disk 113can be seen with tab 117. FIG. 14 shows a view of slot 125 as it is cutinto the bore of the body 101, termination shelf 127 is shown in FIG. 13along O-ring groove 116 and snap ring 119. Rotational stop 118,interfaces with rotation stop 312, is located at the proximal edge 121of body 101. Rotational stop 118 works in conjunction with rotation stop312 providing the user a positive stop to know when the user has fullyopened or closed the valve. In this particular example rotation stop 312interfaces with rotational stop 118 and provides the user with anapproximate 300° rotation. In other embodiments the rotation stop 312and rotational stop 118 can limit the user to 180° of rotation. Inembodiment of the valve has a tactile feel so that each incrementalrotation through guide 105 of the valve can have an indent and detentcombination so that the user can feels the rotation and notice that eachtactile bump represents a number of degrees.

FIGS. 15 and 15A shows a detail the primary control disk where there aretwo openings. The primary control disk 113 that has two 90° angularsections or openings in the face of the disk. FIGS. 16 and 16A show thematching secondary control disk 315 having two 90° angular sections oropenings in the face of the desk. FIGS. 15 and 16 disclose disks withtwo 90° circular segments where the radius of the segment is less thanthe radius of the disk. The radius and chord sections of each of thecircular segment on the primary and secondary control disk must becoincident. The segments are cut out of the where the operator has 180°to go between any of the two extremes, such as 180° from shut off toshut off or 180° from full-flow to full flow. There is no limit to thenumber of angular sections on a particular disk so long as the disk hasan equal number of closed sections that will interface with a similarnumber of sections on the secondary disk so that the valve cancompletely shut off the flow of fluids through the valve.

FIGS. 17 and 17A show the variable Cv disk 415 that can be used as anembodiment to this device. The Cv is defined by the geometry of thearc's radius and chord. As can be seen disk 415 works with primary disk113, where that the design of disk 415 is unique to a defined Cv ormaximum flow. The variable Cv Disk 415 has a crescent shaped arcs wherethe major arc has a defined diameter based on the diameter of disk and aminor arc of lesser diameter is tangentially placed against first arc,and the surface area of the opening defines the maximum flow. Disk 415is factory set for example to 5 gallons per minute, so that the maximumflow through the valve is set by the disk 415. The rotation of thisstyle of desk is 180°. The interface between Cv disk 415 and primarydisk 113, is that disk 113 rotates about the fixed Cv disk regulatingflow up to the maximum flow rate as described by the arcs through arotation of 180°.

FIGS. 18 and 19 detail an embodiment where a set of disks selected bythe user sets a particular Cv from the factory and the valve can rotateup to 300°. With this increase in angular rotation, a more finiteadjustability is introduced into the valve and the design of secondarydisk 415A allows for a more linear relationship between the percentageof the valve opening to the percentage of maximum flow of fluids throughthe valve. Disk 113A is similar in function as primary disk 113 and disk415A is similar in design and function as secondary disk 415. The radiusof the major arc is less than the radius of the secondary disk 41 5A andthe minor arc is not tangentially located but is more centrally locatedand is defined mathematically according to the surface area desiredbased on the maximum Cv or flow rate required of the valve. The valvebody, using rotation stops 118 and 312, allows the user a finer controlof the valve through the entire adjustment range of up to 300°.

Another embodiment, not shown on the drawings is the addition of apiezometer ring or averaging annulus ring in place of low pressuresensing ring 108. This piezometer ring is used when the valve is notlocated on a length of pipe that is sufficiently for a distance toaccurately measure the pressure differential with a regular circularcylindrically shaped venturi sending ring 108. The concept of thepiezometer ring is to create a much finer ability to more accuratelysensing the low pressure so that the valve can operate with a higherdegree of accuracy.

An embodiment utilizing a two piece design in detailed in drawing FIG.20 through 27. In this embodiment, the body does not rotate about theflow of the fluid, but contains the principal elements of having thepressure test ports to high and low side pressures along with a venture,but the main axial body is replaced with an flow control disk carrierwhich functions in the same manner as the body 101 as in the principledisclosure in the co-pending application. This embodiment introduces avalve that is more compact and easier to install. This embodimentutilizes the two flow control disk, 113 and 315, but can also utilizethe combination of primary flow control disk 113 and secondary disk 415Awith the variable Cv style of disk. In this embodiment the inlet isdefined by inlet section 160 which is in embodiment is actually thedistal portion of body portion 150, which is adapted for interface withan existing piping system. The connection to the piping system isthrough a coupling means 161, as shown in FIG. 25 where the means are athreaded connection, but can adapted to any style of interface required.Body 150 contains two pressure sensing ports as in the principle design,with low pressure sensing port 103 on the left side of body 150 and highpressure sensing port 102 on the right side of body 150. These ports areadapted to receive a pressure sensing probe. In this instance, pressuresensing probe 152 is threadably connected to port 102 which is adaptedwith mating threads, and port 103 is adapted to receive probe 153. Saidprobes 152 and 153 can also be of the type to sense temperature as wellas pressure. Unique to this embodiment is adjustment slot 155 which isadapted to receive adjustment means 512, which in this disclosure is acap style screw which when tightened into internally located flowcontrol carrier 500 prevents movement along said slot 155. Body 150 isadapted to receive outlet section 350 on the proximal end of body 150,which in this disclosure are threadably connected to distal end ofoutlet 350 along interface section 365. Outlet 350 is this disclosure isthreadably adapted to interface with existing piping structure throughthreaded opening 303.

FIG. 24 details the direction of cross-sections seen in FIGS. 25 and 26.The cross-sections disclose the interior of this embodiment. Similar tothe initial disclosure, as the fluid enters past coupling means 161 itpasses through fluid channel 111 into venturi 110 and into low pressuresensing ring 108. Fluid channel 111 is where high pressure is sensedthrough high pressure port hole 107 as seen in FIG. 26, port hole 107being in fluid communication with port 102, where probe 152 will measurelow pressure, temperature or whatever variable needed. Low pressuresensing port 106, as seen in FIG. 25, is located in low pressure sensingring 108, where port 106 is in fluid communication with port 103 wheresensing probe 153 will sense low pressure, temperature or whatevervariable needed. Immediately appurtenant to low pressure sensing ring isprimary flow control disk 113 which contains locating tabs 117, wheretabs 117 interface with location slots 122 to securely hold disk 113 inplace and to prevent it's rotation when the secondary disk 315 rotates.

Flow control carrier 500 has proximally located receiving slots 502 thatwill interface with tabs 316 of secondary flow control disk 315. It isthe interface between the openings of primary flow control disk 113 andthe openings of secondary flow control disk 315 that regulates the flowof fluid through the valve. It is critical to understand that the shapeof the openings in the secondary flow control disks can either bedesigned as angular segments or through a variable Cv Disk 415 that hasa crescent shaped arcs where the major arc has a defined diameter basedon the diameter of disk and a minor arc of lesser diameter istangentially placed against first arc, and the surface area of theopening defines the maximum flow. Carrier 500 is a free floatingapparatus completely contained between body 150 and outlet section 350,whereby the carrier 500 is free to rotate about the central axis commonto the fluid flow. Carrier 500 has rotation means 512 attached to theexterior surface of carrier 500 through carrier rotational meanssecurement means 513. In this disclosure, a cap style screw 512 isthreadably attached to carrier 500 through securement threaded hole 513.Screw 512 has a sufficiently narrow body which will be able carrier 150to rotate freely through body rotational adjustment slot 155, said slot155 being along the circumference of body 150 extending from theexterior through the interior surface of said body. Screw 512 is tightenagainst the exterior of slot 155 thereby preventing unwanted rotationalmovement of carrier 500 once the user has set the valve. The adjustmentslot 155 is of a length to limit the user to adjust the flow fromcomplete shutoff to maximum flow with positive stops at each extreme.The length of rotational adjustment slot corresponds to the shape anddimension of the segment section of the secondary disk 315 or 415. It isthe rotation of the carrier through the rotation mean, said rotationbeing axially aligned to the flow of fluid through the valve which has adirect correlation to the amount of flow output through outlet section350. It can be designed so that incremental marks (not shown) are placedalong the exterior of adjustment slot 150 to show percentage of openingthat has been accomplished through the rotation of the screw.Additionally, it is desirable to have detents placed along adjustmentslot 155 so that the user can have a tactile response to the percentageopen that the valve has obtained as the valve may be in a location wherevisible indicators are not possible,

The two styles of the secondary flow control disks as shown FIG. 15through 19A dictate the length of the adjustment slot 155, where thestart and stop limits are demarcated preventing the user from exceedingthe limits, Depending on the shape of the openings, the operator canhave a 1/4 turn ball valve like control from complete shutoff to maximumflow. The adjustment slot will be longer should a fixed Cv style of diskbe used.

Carrier 500 is isolated from body 150 and outlet 350 and is securedagainst leakage by two sets of O-rings. Distal O-ring 520 seals againstcarrier 500 and body 150 contained in O-ring groove 157. O-Ring 150 notonly provides sealing to prevent blow-by past the secondary flow controldisk but also provides a centering means to hold carrier 500 directlyalong the axis of fluid flow. Proximal O-ring 521 seals between carrier500 and outlet section contained in groove 363. O-ring 521 not onlyprevents the flow of fluids outside of the prescribed fluid flow channel510 and central outlet bore 304 but also serves as a compression meansinsuring that the secondary and primary disks are in compressivecontact.

It can be appreciated by those appropriately skilled in the art thatchanges, modifications or embodiments can be made to this inventionwithout departing from the spirit, principles, theories, ideas orconceptions that have been disclosed in the foregoing. It is hereinrecognized that the embodiments disclosed by this description of thebest mode of practicing this invention, which will be hereafterdescribed in their full breadth in the claims and equivalents thereof.

We claim:
 1. A valve comprising: a valve body, an inlet end, and anoutlet end, and a bore extending through the inlet end, the valve body,and the outlet end, said valve body defining a longitudinal axis of thevalve; a first disk disposed within the valve body, disposedperpendicularly to the axis, said first disk have a first aperturethrough which fluid can flow, said first disk being rotationally fixedrelative to the valve body; a second disk disposed within the bore ofthe valve body, disposed perpendicularly to the axis, said second diskhave a second aperture through which fluid can flow, said second diskbeing rotatably disposed relative to the valve body; means for rotatingthe first disk relative to the second disk to move the first apertureinto alignment with the second aperture to allow flow through the firstand second apertures and to move the first aperture out of alignmentwith the second aperture to prevent flow through the first and secondapertures; and a Venturi disposed within the body section, spaced fromand proximate the first and second disks.
 2. The valve of claim 1,wherein: the first disk is rotationally fixed to the valve body, and thesecond disk is rotatable relative to the valve body.
 3. The valve ofclaim 2, wherein: the second disk is rotationally fixed to an end. 4.The valve of claim 1, further comprising: a carrier rotatably disposedwithin the bore of the valve body and rotationally fixed to the seconddisk.
 5. The valve of claim 4, wherein: a carrier is rotationally fixedto the means for rotating, and disposed between the means for rotatingand the second disk.
 6. The valve of claim 1, wherein: an interior borewall rotationally fixed to the valve, said interior bore wall having atleast one longitudinally oriented slot, wherein the first disk comprisesat least one longitudinally extending locking tab sized and dimensionedto fit into the longitudinally oriented slot, whereby rotation of thefirst disk within the valve is prevented.
 7. The valve of claim 1,wherein: the valve body is fixed to the inlet end and the outlet end,and the means for rotating is rotatable relative to the valve body. 8.The valve of claim 7, wherein: the valve body is rotatable relative tothe inlet end and the outlet end.
 9. The valve of claim 1, wherein: thefirst disk is rotationally fixed to the valve body, and the means forrotating comprises the valve body rotatable relative to the inlet endand the outlet end.
 10. The valve of claim 9, wherein: the second diskis rotationally fixed to an end.
 11. A valve comprising: a valve body,an inlet end, and an outlet end, and a bore extending through the inletend, the valve body, and the outlet end, said valve body defining alongitudinal axis of the valve; a first disk disposed within the valvebody, disposed perpendicularly to the axis, said first disk have a firstaperture through which fluid can flow, said first disk beingrotationally fixed relative to the valve body; a second disk disposedwithin the bore of the valve body, disposed perpendicularly to the axis,said second disk have a second aperture through which fluid can flow,said second disk being rotatable relative to the valve body; means forrotating the first disk relative to the second disk to move the firstaperture into alignment with the second aperture to allow flow throughthe first and second apertures and to move the first aperture out ofalignment with the second aperture to prevent flow through the first andsecond apertures; and a piezometer ring disposed in the bore of thevalve body.
 12. The valve of claim 11, wherein: the first disk isrotationally fixed to the valve body, and the second disk is rotatablerelative to the valve body.
 13. The valve of claim 12, wherein: thesecond disk is rotationally fixed to an end.
 14. The valve of claim 11,further comprising: a carrier rotatably disposed within the bore of thevalve body and rotationally fixed to the second disk.
 15. The valve ofclaim 14, wherein: a carrier is rotationally fixed to the means forrotating, and disposed between the means for rotating and the seconddisk.
 16. The valve of claim 11, further comprising: an interior borewall rotationally fixed to the valve, said interior bore wall having atleast one longitudinally oriented slot, wherein the first disk comprisesat least one longitudinally extending locking tab sized and dimensionedto fit into the longitudinally oriented slot, whereby rotation of thefirst disk within the valve is prevented.
 17. The valve of claim 11,wherein: the valve body is fixed to the inlet end and the outlet end,and the means for rotating is rotatable relative to the valve body. 18.The valve of claim 17, wherein: the valve body is rotatable relative tothe inlet end and the outlet end.
 19. The valve of claim 11, wherein:the first disk is rotationally fixed to the valve body, and the meansfor rotating comprises the valve body rotatable relative to the inletend and the outlet end.
 20. The valve of claim 19, wherein: the seconddisk is rotationally fixed to an end.